Independently controllable transmission mechanism with an identity-ratio series type

ABSTRACT

An independently controllable transmission mechanism with an identity-ratio series type includes a first planetary gear train and a second planetary gear train mechanically connected therewith. The transmission mechanism has a power output end, a transmission control end, a power input end and a free transmission end. The power output end and the transmission control end are provided on the first planetary gear train and the second planetary gear train, respectively. The power input end is provided on the first planetary gear train or the second planetary gear train while the free transmission end is provided on the second planetary gear train or the first planetary gear train. The transmission control end is operated to freely shift the free transmission end as a power input end or a power output end.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of U.S. patent applicationSer. No. 12/547,669, filed Aug. 26, 2009, which is hereby incorporatedby reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to an independently controllabletransmission mechanism. More particularly, the present invention relatesto the independently controllable transmission mechanism utilizing twoplanetary gear trains for variably controlling power input and output.

2. Description of the Related Art

Taiwanese Patent Pub. No. 1242521 discloses a conventional gearboxstructure for vehicles, including a main shaft on which to provide aslide. A forward gear and a drive gear are arranged at each side of theslide. A transmission shaft is provided with a reverse slide and acombination of a backward bevel gear and a forward bevel gear adjacentto the reverse slide. A final gear shaft is arranged between thebackward bevel gear and the forward bevel gear. The forward gear and thedrive gear are also arranged between the backward bevel gear and theforward bevel gear such that a width of the gearbox can be significantlyreduced. Furthermore, the backward bevel gear and the forward bevel gearare used to engage with a transmission bevel gear provided on the finalgear shaft so as to minimize the size of the gearbox. With regard to theproblematic aspects naturally occurring during use of the gearboxsystem, the transmission in the gearbox system is susceptible toinefficiency due to the fact that the slide must result in frictionalslide movements in the gearbox.

U.S. Pat. No. 6,387,004, entitled “Continuously Variable Transmission,”discloses a continuously variable transmission system, including a firstplanetary gear train and a second planetary gear train. The firstplanetary gear train and the second planetary gear train are used tocorrespondingly transmit powers, which are generated from a first motorand a second motor, to a transmission shaft. However, the primaryproblem with such a transmission system is due to the fact that thepowers generated from the first motor and the second motor must beconstantly transmitted to the single transmission shaft via the firstplanetary gear train and the second planetary gear train. In thismanner, the transmission shaft is fixedly designated as a single powerinput end while the first motor and the second motor are designated astwo power input ends. The transmission system, however, cannot befunctioned to variably control the power output. Hence, there is a needof providing an independently controllable transmission mechanism forvariably controlling the power input, and for variably controlling thepower output.

As is described in greater detail below, the present invention intendsto provide an independently controllable transmission mechanismutilizing two planetary gear trains for variably controlling power inputand output. The transmission mechanism includes a power output end, atransmission control end, a power input end and a free transmission end.The transmission mechanism is capable of shifting the free transmissionend between a power input end and a power output end for independentlycontrolling the power transmission. The transmission mechanism of thepresent invention can avoid using any additional frictionally slidingmember so as to achieve increasing the efficiency of power transmission.

SUMMARY OF THE INVENTION

The primary objective of this invention is to provide an independentlycontrollable transmission mechanism, wherein two planetary gear trainsare utilized to variably control power input and output. Thetransmission mechanism includes a power output end, a transmissioncontrol end, a power input end and a free transmission end. Thetransmission mechanism is capable of shifting the free transmission endbetween a power input end and a power output end for independentlycontrolling the power transmission. Accordingly, independentlycontrolling the power transmission of the transmission mechanism can besuccessfully achieved.

Another objective of this invention is to provide an independentlycontrollable transmission mechanism, wherein two planetary gear trainsare utilized to variably control power input and output. No additionalfrictionally sliding member is utilized in the transmission mechanism.Accordingly, the efficiency of the power transmission of the presentinvention can be successfully increased.

The independently controllable transmission mechanism in accordance withan aspect of the present invention includes a first planetary gear trainand a second planetary gear train. The independently controllabletransmission mechanism has a first power output end, a transmissioncontrol end, a first power input end and a free transmission end. Thepower output end is provided on the first planetary gear train and thetransmission control end is provided on the second planetary gear train.The free transmission end is provided on the second planetary gear trainor the first planetary gear train while the power input end is providedon the first planetary gear train or the second planetary gear train.The transmission control end is used to control the free transmissionend to be functioned as a second power input end or a second poweroutput end (i.e. to controllably shift the free transmission end as thesecond power input end or the second power output end).

In a separate aspect of the present invention, the first planetary geartrain includes a first rotational axle, a second rotational axle and athird rotational axle.

In a further separate aspect of the present invention, the firstrotational axle of the first planetary gear train performs as the firstpower output end.

In a yet further separate aspect of the present invention, the secondrotational axle of the first planetary gear train performs as the freetransmission end or the first power input end.

In a yet further separate aspect of the present invention, the thirdrotational axle of the first planetary gear train connects with thesecond planetary gear train. In a yet further separate aspect of thepresent invention, the first planetary gear train has a positive speedratio.

In a yet further separate aspect of the present invention, the secondplanetary gear train includes a first rotational axle, a secondrotational axle and a third rotational axle.

In a yet further separate aspect of the present invention, the firstrotational axle of the second planetary gear train performs as thetransmission control end.

In a yet further separate aspect of the present invention, the secondrotational axle of the second planetary gear train performs as the firstpower input end or the free transmission end.

In a yet further separate aspect of the present invention, the thirdrotational axle of the second planetary gear train connects with thefirst planetary gear train.

In a yet further separate aspect of the present invention, the secondplanetary gear train has a negative speed ratio.

Further scope of the applicability of the present invention will becomeapparent from the detailed description given hereinafter. However, itshould be understood that the detailed description and specificexamples, while indicating preferred embodiments of the invention, aregiven by way of illustration only, since various will become apparent tothose skilled in the art from this detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will become more fully understood from thedetailed description given hereinbelow and the accompanying drawingswhich are given by way of illustration only, and thus are not limitativeof the present invention, and wherein:

FIGS. 1A and 1B are schematic views of an independently controllabletransmission mechanism with an identity-ratio series type in accordancewith first and second preferred embodiments of the present invention.FIGS. 2A and 2B are internal schematic views of the independentlycontrollable transmission mechanism with the identity-ratio series type,depicted in FIGS. 1A and 1B, in accordance with the first and secondpreferred embodiments of the present invention.

FIGS. 3A and 3B are similar internal schematic views of planetary geartrains applied in the independently controllable transmission mechanismin accordance with the preferred embodiment of the present invention.

FIGS. 4 through 28 are similar internal schematic views of severalcombinations of two planetary gear trains formed in the independentlycontrollable transmission mechanism in accordance with a third throughtwenty-seventh embodiments of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

It is noted that an independently controllable transmission mechanismwith an identity-ratio series type in accordance with the preferredembodiment of the present invention can be a wide variety oftransmission-related mechanisms applicable to transmission gearboxes ofocean power generators (e.g., tidal power generator, wave powergenerator or ocean current power generator), wind power generators orhybrid vehicles, which are not limitative of the present invention.

FIGS. 1A and 1B illustrate an independently controllable transmissionmechanism with an identity-ratio series type in accordance with firstand second preferred embodiments of the present invention; FIGS. 2A and2B illustrate internal schematic views of the independently controllabletransmission mechanism with the identity-ratio series type, depicted inFIGS. 1A and 1B, in accordance with the first and second preferredembodiments of the present invention. Referring to FIGS. 1A, 1B, 2A and2B, the independently controllable transmission mechanism of the firstand second embodiments include a first planetary gear train 1 and asecond planetary gear train 2 mechanically connected thereto.

Referring again to FIGS. 1A, 1B, 2A and 2B, the independentlycontrollable transmission mechanism of the first and second embodimentshave a first power output end, a transmission control end, a first powerinput end and a free transmission end which are separately arrangedthereon. The first power input end and the first power output endperform as a permanent input end and a permanent output end,respectively.

Referring again to FIGS. 1A and 2A, in the independently controllabletransmission mechanism of the first embodiment the first power outputend and the free transmission end correspond to the first planetary geartrain 1 while the transmission control end and the first power input endcorrespond to the second planetary gear train.

Referring again to FIGS. 1B and 2B, in the independently controllabletransmission mechanism of the second embodiment the first power outputend and the first power input end correspond to the first planetary geartrain 1 while the transmission control end and the free transmission endcorrespond to the second planetary gear train.

Still referring to FIG. 2A, in the first embodiment the first planetarygear train 1 has a first rotational axle identified as OP, a secondrotational axle identified as AD and a third rotational axle identifiedas AE. The first rotational axle OP performs as the first power outputend of the transmission mechanism. The second rotational axle ADperforms as the free transmission end of the transmission mechanism. Thethird rotational axle AE connects with the second planetary gear train2. Correspondingly, the second planetary gear train 2 includes a firstrotational axle identified as CR, a second rotational axle identified asBD and a third rotational axle identified as BE. The first rotationalaxle CR performs as the transmission control end of the transmissionmechanism. The second rotational axle BD performs as the first powerinput end of the transmission mechanism. The third rotational axle BEconnects with the first planetary gear train 1.

Still referring to FIG. 2B, in the second embodiment the first planetarygear train 1 has a first rotational axle identified as OP, a secondrotational axle identified as AD and a third rotational axle identifiedas AE. The first rotational axle OP performs as the first power outputend of the transmission mechanism. The second rotational axle ADperforms as the first power input end of the transmission mechanism. Thethird rotational axle AE connects with the second planetary gear train2. Correspondingly, the second planetary gear train 2 includes a firstrotational axle identified as CR, a second rotational axle identified asBD and a third rotational axle identified as BE. The first rotationalaxle CR performs as the transmission control end of the transmissionmechanism. The second rotational axle BD performs as the freetransmission end of the transmission mechanism. The third rotationalaxle BE connects with the first planetary gear train 1.

Referring again to FIGS. 1A and 2A, in the independently controllabletransmission mechanism of the first embodiment the transmission controlend (first rotational axle CR) of the second planetary gear train 2 isused to control the free transmission end (second rotational axle AD) ofthe first planetary gear train 1 to be functioned as a second powerinput end or a second power output end (i.e. to controllably shift thefree transmission end AD as the second power input end or the secondpower output end). When the free transmission end AD is functioned asthe second power input end, the first power input end BD of the secondplanetary gear train 2 and the free transmission end AD of the firstplanetary gear train 1 are capable of synchronously inputting power fromdifferent sources. Conversely, When the free transmission end AD isfunctioned as the second power output end, the first power output end OPand the free transmission end AD of the first planetary gear train 1 arecapable of synchronously outputting power from the transmissionmechanism.

Referring again to FIGS. 1B and 2B, in the independently controllabletransmission mechanism of the second embodiment the transmission controlend (first rotational axle CR) of the second planetary gear train 2 isused to control the free transmission end (second rotational axle BD) ofthe second planetary gear train 2 to be functioned as a second powerinput end or a second power output end (i.e. to controllably shift thefree transmission end BD as the second power input end or the secondpower output end). When the free transmission end BD is functioned asthe second power input end, the free transmission end BD of the secondplanetary gear train 2 and the first power input end AD of the firstplanetary gear train 1 are capable of synchronously inputting power fromdifferent sources. Conversely, When the free transmission end BD isfunctioned as the second power output end, the first power output end OPof the first planetary gear train 1 and the free transmission end BD ofthe second planetary gear train 2 are capable of synchronouslyoutputting power from the transmission mechanism.

FIGS. 3A and 3B illustrate the planetary gear trains applied in theindependently controllable transmission mechanism in accordance with thepreferred embodiment of the present invention, wherein two examples ofinternal configurations of the planetary gear trains are shown, whichare not limitative of the present invention.

Turning now to FIG. 3A, the first example of the planetary gear trainincludes a sun gear identified as ps1, a sun-gear rotational axleidentified as pss1, a central gear identified as ps2, a central-gearrotational axle identified as pss2, at least one compound planetary gearset formed with a first planetary gear identified as pp1 and a secondplanetary gear identified as pp2, and a planet gear carrier identifiedas pa. The first planetary gear identified as pp1 and the secondplanetary gear identified as pp2 are correspondingly engaged with thesun gear psi. and the central gear ps2. The sun-gear rotational axlepss1 and the planet gear carrier pa are in perfect alignment with eachother and coaxial. When the planet gear carrier pa is fixed, thesun-gear rotational axle pss1 and the central-gear rotational axle pss2have same rotational directions and a positive ratio of rotationalspeeds. As is explained above, the planetary gear train is selected froma planetary gear train with a positive speed ratio. Referring again toFIGS. 2A, 2B and 3A, the sun-gear rotational axle pss1, the central-gearrotational axle pss2 and the planet gear carrier pa can be performed asthe first rotational axle OP, the second rotational axle AD and thethird rotational axle AE of the first planetary gear train 1 .Alternatively, the sun-gear rotational axle pss1, the central-gearrotational axle pss2 and the planet gear carrier pa can be performed asthe first rotational axle CR, the second rotational axle BD and thethird rotational axle BE of the second planetary gear train 2.

Turning now to FIG. 3B, the second example of the planetary gear trainincludes a sun gear identified as ns, a sun-gear rotational axleidentified as nss, a ring gear identified as nr, a ring-gear rotationalaxle identified as nrs, at least one planetary gear identified as np anda planet gear carrier identified as na. When the planet gear carrier nais fixed, the sun-gear rotational axle nss and the ring-gear rotationalaxle nrs are rotated in reverse directions and have a negative ratio ofrotational speeds. As is explained above, the planetary gear train isselected from a planetary gear train with a negative speed ratio.

Referring again to FIGS. 2A, 2B and 3B, the sun-gear rotational axlenss, the ring-gear rotational axle nrs and the planet gear carrier nacan be performed as the first rotational axle OP, the second rotationalaxle AD and the third rotational axle AE of the first planetary geartrain 1. Alternatively, the sun-gear rotational axle nss, the ring-gearrotational axle nrs and the planet gear carrier na can be performed asthe first rotational axle CR, the second rotational axle BD and thethird rotational axle BE of the second planetary gear train 2.

Referring back to FIGS. 2A and 2B, the relation between the speeds ofthe first rotational axle OP of the first planetary gear train 1 (i.e.first power output end) and the first rotational axle CR of the secondplanetary gear train 2 (i.e. transmission control end) in accordancewith the present invention are

$\frac{n_{OP}}{n_{CR}} = 1$

given as:

where n_(op) and n_(CR) are speeds of the first rotational axle OP ofthe first planetary gear train 1 (i.e. first power output end) and thefirst rotational axle CR of the second planetary gear train 2 (i.e.transmission control end).

Furthermore, the relation between the speeds of the second rotationalaxle AD of the first planetary gear train 1 and the third rotationalaxle BE of the second planetary gear train 2 in accordance with thepresent invention are

$\frac{n_{AD}}{n_{BE}} = 1$

given as:

where n_(AD) and n_(BE) are speeds of the second rotational axle AD ofthe first planetary gear train 1 and the third rotational axle BE of thesecond planetary gear train 2.

Furthermore, the relation between the speeds of the second rotationalaxle BD of the second planetary gear train 2 and the third rotationalaxle AE of the first planetary gear train 1 in accordance with thepresent invention are

$\frac{n_{BD}}{n_{AE}} = 1$

given as:

where n_(BD) and n_(AE) are speeds of the second rotational axle BD ofthe second planetary gear train 2 and the third rotational axle AE ofthe first planetary gear train 1.

FIGS. 4 through 28 illustrate several combinations of two planetary geartrains formed in the independently controllable transmission mechanismin accordance with a third through twenty-seventh embodiments of thepresent invention, wherein twenty five embodiments of the transmissionmechanisms are shown, which are not limitative of the present invention.Turning now to FIGS. 4 through 28, the transmission mechanism includestwo planetary gear trains (dotted lines in two circles, which correspondto FIGS. 3A and 3B). As has been described in FIGS. 3A and 3B, thedetailed configurations of the planetary gear trains in FIGS. 4 through28 will not be described for the sake of clarity.

Referring again to FIGS. 2A, 2B and 4, in the third embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of two planetarygear trains each of which has a positive speed ratio. Two sun-gearrotational axles pss1A, pss1B of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). The two planetgear carriers have a common rotational axle pa while the two centralgears ps2A, ps2B have a common rotational axle pss2. The two commonrotational axles pa, pss2 perform as the second rotational axle AD ofthe first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 5, in the fourth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of a planetary geartrain having a positive speed ratio and a planetary gear train having anegative speed ratio. Two sun-gear rotational axles pss1, nss of the twoplanetary gear trains perform as the first power output end of the firstplanetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). The two planet gear carriers have a commonrotational axle pa while the central gear ps2 and the ring gear nr havea common rotational axle nrs. The two common rotational axles pa, nrsperform as the second rotational axle AD of the first planetary geartrain 1 (free transmission end in FIG. 2A or first power input end inFIG. 2B) and the second rotational axle BD of the second planetary geartrain 2 (first power input end in FIG. 2A or free transmission end inFIG. 2B).

Referring again to FIGS. 2A, 2B and 6, in the fifth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of a planetary geartrain having a positive speed ratio and a planetary gear train having anegative speed ratio. A sun-gear rotational axle pss and a ring-gearrotational axle nrs of the two planetary gear trains perform as thefirst power output end of the first planetary gear train 1 (i.e. firstrotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). The two planetgear carriers have a common rotational axle pa while the central gearps2 and the sun gear ns have a common rotational axle nss. The twocommon rotational axles pa, nss perform as the second rotational axle ADof the first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 7, in the sixth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of two planetarygear trains each of which has a negative speed ratio. Two sun-gearrotational axles nssA, nssB of the two planetary gear trains perform asthe first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). The two planetgear carriers have a common rotational axle na while the two ring gearsnrA, nrB have a common rotational axle nrs. The two common rotationalaxles na, nrs perform as the second rotational axle AD of the firstplanetary gear train 1 (free transmission end in FIG. 2A or first powerinput end in FIG. 2B) and the second rotational axle BD of the secondplanetary gear train 2 (first power input end in FIG. 2A or freetransmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 8, in the seventh embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of two planetarygear trains each of which has a negative speed ratio. Two ring-gearrotational axles nrsA, nrsB of the two planetary gear trains perform asthe first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). The two planetgear carriers have a common rotational axle na while the two sun gearnsA, nsB have a common rotational axle nss. The two common rotationalaxles na, nss perform as the second rotational axle AD of the firstplanetary gear train 1 (free transmission end in FIG. 2A or first powerinput end in FIG. 2B) and the second rotational axle BD of the secondplanetary gear train 2 (first power input end in FIG. 2A or freetransmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 9, in the eighth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of two planetarygear trains each of which has a negative speed ratio. A sun-gearrotational axle nssA and a ring-gear rotational axle nrs of the twoplanetary gear trains perform as the first power output end of the firstplanetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). The two planet gear carriers have a commonrotational axle na while the ring gear nrA and the sun gear nsB have acommon rotational axle nssB. The two common rotational axles na, nssBperform as the second rotational axle AD of the first planetary geartrain 1 (free transmission end in FIG. 2A or first power input end inFIG. 2B) and the second rotational axle BD of the second planetary geartrain 2 (first power input end in FIG. 2A or free transmission end inFIG. 2B).

Referring again to FIGS. 2A, 2B and 10, in the ninth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of two planetarygear trains each of which has a positive speed ratio. A sun-gearrotational axle pss1 and a planet gear carrier paB of the two planetarygear trains perform as the first power output end of the first planetarygear train 1 (i.e. first rotational axle OP) and the transmissioncontrol end of the second planetary gear train 2 (i.e. first rotationalaxle CR). A planet gear carrier and a sun gear ps1B of the planetarygear trains have a common rotational axle paA while the two centralgears ps2A, ps2B have a common rotational axle pss2. The two commonrotational axles paA, pss2 perform as the second rotational axle AD ofthe first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 11, in the tenth embodiment, the twoplanetary gear trains correspond to the first planetary gear train 1 andthe second planetary gear train 2 and are comprised of two planetarygear trains each of which has a positive speed ratio. A sun-gearrotational axle pss1A and a central-gear rotational axle pss2B of thetwo planetary gear trains perform as the first power output end of thefirst planetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A central gear ps2A and a planet gear carrierof the planetary gear trains have a common rotational axle pss2A while aplanet gear carrier and a sun gear ps1B of the planetary gear trainshave a common rotational axle pss1B. The two common rotational axlespss2A, pss1B perform as the second rotational axle AD of the firstplanetary gear train 1 (free transmission end in FIG. 2A or first powerinput end in FIG. 2B) and the second rotational axle BD of the secondplanetary gear train 2 (first power input end in FIG. 2A or freetransmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 12, in the eleventh embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of a planetarygear train having a positive speed ratio and a planetary gear trainhaving a negative speed ratio. A sun-gear rotational axle pss1 and aplanet gear carrier na of the two planetary gear trains perform as thefirst power output end of the first planetary gear train 1 (i.e. firstrotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A central gearps2 and a ring gear nr of the planetary gear trains have a commonrotational axle pss2 while a planet gear carrier and a sun gear ns ofthe planetary gear trains have a common rotational axle nss. The twocommon rotational axles pss2, nss perform as the second rotational axleAD of the first planetary gear train 1 (free transmission end in FIG. 2Aor first power input end in FIG. 2B) and the second rotational axle BDof the second planetary gear train 2 (first power input end in FIG. 2Aor free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 13, in the twelfth embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of a planetarygear train having a positive speed ratio and a planetary gear trainhaving a negative speed ratio. A sun-gear rotational axle pss1 and aplanet gear carrier na of the two planetary gear trains perform as thefirst power output end of the first planetary gear train 1 (i.e. firstrotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A planet gearcarrier and a ring gear nr of the planetary gear trains have a commonrotational axle pa while a central gear ps2 and a sun gear ns of theplanetary gear trains have a common rotational axle nss. The two commonrotational axles pa, nss perform as the second rotational axle AD of thefirst planetary gear train 1 (free transmission end in FIG. 2A or firstpower input end in FIG. 2B) and the second rotational axle BD of thesecond planetary gear train 2 (first power input end in FIG. 2A or freetransmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 14, in the thirteenth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of aplanetary gear train having a positive speed ratio and a planetary geartrain having a negative speed ratio. A planet gear carrier pa and asun-gear rotational axle nss of the two planetary gear trains perform asthe first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A sun gear psiand a planet gear carrier of the planetary gear trains have a commonrotational axle pss1 while a central gear ps2 and a ring gear nr of theplanetary gear trains have a common rotational axle nrs. The two commonrotational axles pss1, nrs perform as the second rotational axle AD ofthe first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 15, in the fourteenth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of aplanetary gear train having a positive speed ratio and a planetary geartrain having a negative speed ratio. A planet gear carrier pa and aring-gear rotational axle nrs of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A sun gear psiand a planet gear carrier of the planetary gear trains have a commonrotational axle pss1 while a central gear ps2 and a sun gear ns of theplanetary gear trains have a common rotational axle nss. The two commonrotational axles pss1, nss perform as the second rotational axle AD ofthe first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 16, in the fifteenth embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of a planetarygear train having a positive speed ratio and a planetary gear trainhaving a negative speed ratio. Two sun-gear rotational axles pss1, nssof the two planetary gear trains perform as the first power output endof the first planetary gear train 1 (i.e. first rotational axle OP) andthe transmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A planet gear carrier and a ring gear nr ofthe planetary gear trains have a common rotational axle pa while acentral gear ps2 and a planet gear carrier of the planetary gear trainshave a common rotational axle na. The two common rotational axles pa, naperform as the second rotational axle AD of the first planetary geartrain 1 (free transmission end in FIG. 2A or first power input end inFIG. 2B) and the second rotational axle BD of the second planetary geartrain 2 (first power input end in FIG. 2A or free transmission end inFIG. 2B).

Referring again to FIGS. 2A, 2B and 17, in the sixteenth embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of a planetarygear train having a positive speed ratio and a planetary gear trainhaving a negative speed ratio. A sun-gear rotational axle pss and aring-gear rotational axle nrs of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A planet gearcarrier and a sun gear ns of the planetary gear trains have a commonrotational axle pa while a central gear ps2 and a planet gear carrier ofthe planetary gear trains have a common rotational axle na. The twocommon rotational axles pa, na perform as the second rotational axle ADof the first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 18, in the seventeenth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Asun-gear rotational axle nss and a planet gear carrier naB of the twoplanetary gear trains perform as the first power output end of the firstplanetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A planet gear carrier and a sun gear nsB ofthe planetary gear trains have a common rotational axle naA while tworing gears nrA, nrB of the planetary gear trains have a commonrotational axle nrs. The two common rotational axles naA, nrs perform asthe second rotational axle AD of the first planetary gear train 1 (freetransmission end in FIG. 2A or first power input end in FIG. 2B) and thesecond rotational axle BD of the second planetary gear train 2 (firstpower input end in FIG. 2A or free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 19, in the eighteenth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Asun-gear rotational axle nssA and a planet gear carrier naB of the twoplanetary gear trains perform as the first power output end of the firstplanetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A planet gear carrier and a ring gear nrB ofthe planetary gear trains have a common rotational axle naA while a ringgear nrA and a sun gear nsB of the planetary gear trains have a commonrotational axle nssB. The two common rotational axles naA, nssB performas the second rotational axle AD of the first planetary gear train 1(free transmission end in FIG. 2A or first power input end in FIG. 2B)and the second rotational axle BD of the second planetary gear train 2(first power input end in FIG. 2A or free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 20, in the nineteenth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Twosun-gear rotational axles nssA, nssB of the two planetary gear trainsperform as the first power output end of the first planetary gear train1 (i.e. first rotational axle OP) and the transmission control end ofthe second planetary gear train 2 (i.e. first rotational axle CR). Aplanet gear carrier and a ring gear nrB of the planetary gear trainshave a common rotational axle naA while a ring gear nrA and a planetgear carrier of the planetary gear trains have a common rotational axlenaB. The two common rotational axles naA, naB perform as the secondrotational axle AD of the first planetary gear train 1 (freetransmission end in FIG. 2A or first power input end in FIG. 2B) and thesecond rotational axle BD of the second planetary gear train 2 (firstpower input end in FIG. 2A or free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 21, in the twentieth embodiment, thetwo planetary gear trains correspond to the first planetary gear train 1and the second planetary gear train 2 and are comprised of two planetarygear trains each of which has a negative speed ratio. Two ring-gearrotational axles nrsA, nrsB of the two planetary gear trains perform asthe first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A planet gearcarrier and a sun gear nsB of the planetary gear trains have a commonrotational axle naA while a sun gear nsA and a planet gear carrier ofthe planetary gear trains have a common rotational axle naB. The twocommon rotational axles naA, naB perform as the second rotational axleAD of the first planetary gear train 1 (free transmission end in FIG. 2Aor first power input end in FIG. 2B) and the second rotational axle BDof the second planetary gear train 2 (first power input end in FIG. 2Aor free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 22, in the twenty-first embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Asun-gear rotational axles nss and a ring-gear rotational axle nrs of thetwo planetary gear trains perform as the first power output end of thefirst planetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A planet gear carrier and a sun gear nsB ofthe planetary gear trains have a common rotational axle naA while a ringgear nrA and a planet gear carrier of the planetary gear trains have acommon rotational axle naB. The two common rotational axles naA, naBperform as the second rotational axle AD of the first planetary geartrain 1 (free transmission end in FIG. 2A or first power input end inFIG. 2B) and the second rotational axle BD of the second planetary geartrain 2 (first power input end in FIG. 2A or free transmission end inFIG. 2B).

Referring again to FIGS. 2A, 2B and 23, in the twenty-second embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a positive speed ratio. Twoplanet gear carriers paA, paB of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). Two sun gearsps1A, ps1B of the planetary gear trains have a common rotational axlepss1 while two central gears ps2A, ps2B of the planetary gear trainshave a common rotational axle pss2. The two common rotational axlespss1, pss2 perform as the second rotational axle AD of the firstplanetary gear train 1 (free transmission end in FIG. 2A or first powerinput end in FIG. 2B) and the second rotational axle BD of the secondplanetary gear train 2 (first power input end in FIG. 2A or freetransmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 24, in the twenty-third embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of aplanetary gear train having a positive speed ratio and a planetary geartrain having a negative speed ratio. Two planet gear carriers pa, na ofthe two planetary gear trains perform as the first power output end ofthe first planetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). Two sun gears psi, ns of the planetary geartrains have a common rotational axle pss1 while a central gear ps2 and aring gear nr of the planetary gear trains have a common rotational axlenrs. The two common rotational axles pss1, nrs perform as the secondrotational axle AD of the first planetary gear train 1 (freetransmission end in FIG. 2A or first power input end in FIG. 2B) and thesecond rotational axle BD of the second planetary gear train 2 (firstpower input end in FIG. 2A or free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 25, in the twenty-fourth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Twoplanet gear carriers naA, naB of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). Two sun gearsnsA, nsB of the planetary gear trains have a common rotational axle nsswhile two ring gears nrA, nrB of the planetary gear trains have a commonrotational axle nrs. The two common rotational axles nss, nrs perform asthe second rotational axle AD of the first planetary gear train 1 (freetransmission end in FIG. 2A or first power input end in FIG. 2B) and thesecond rotational axle BD of the second planetary gear train 2 (firstpower input end in FIG. 2A or free transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 26, in the twenty-fifth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. Twoplanet gear carriers naA, naB of the two planetary gear trains performas the first power output end of the first planetary gear train 1 (i.e.first rotational axle OP) and the transmission control end of the secondplanetary gear train 2 (i.e. first rotational axle CR). A sun gear nsAand a ring gear nrB of the planetary gear trains have a commonrotational axle nssA while a ring gear nrA and a sun gear nsB of theplanetary gear trains have a common rotational axle nssB. The two commonrotational axles nssA, nssB perform as the second rotational axle AD ofthe first planetary gear train 1 (free transmission end in FIG. 2A orfirst power input end in FIG. 2B) and the second rotational axle BD ofthe second planetary gear train 2 (first power input end in FIG. 2A orfree transmission end in FIG. 2B).

Referring again to FIGS. 2A, 2B and 27, in the twenty-sixth embodiment,the two planetary gear trains correspond to the first planetary geartrain 1 and the second planetary gear train 2 and are comprised of twoplanetary gear trains each of which has a negative speed ratio. A ringgear rotational axle nrs and a planet gear carrier na of the twoplanetary gear trains perform as the first power output end of the firstplanetary gear train 1 (i.e. first rotational axle OP) and thetransmission control end of the second planetary gear train 2 (i.e.first rotational axle CR). A sun gear nsA and a ring gear nrB of theplanetary gear trains have a common rotational axle nssA while a planetgear carrier and a sun gear nsB of the planetary gear trains have acommon rotational axle nssB. The two common rotational axles nssA, nssBperform as the second rotational axle AD of the first planetary geartrain 1 (free transmission end in FIG. 2A or first power input end inFIG. 2B) and the second rotational axle BD of the second planetary geartrain 2 (first power input end in FIG. 2A or free transmission end inFIG. 2B).

Referring again to FIGS. 2A, 2B and 28, in the twenty-seventhembodiment, the two planetary gear trains correspond to the firstplanetary gear train 1 and the second planetary gear train 2 and arecomprised of two planetary gear trains each of which has a negativespeed ratio. A ring gear rotational axle nrsA and a planet gear carrierna of the two planetary gear trains perform as the first power outputend of the first planetary gear train 1 (i.e. first rotational axle OP)and the transmission control end of the second planetary gear train 2(i.e. first rotational axle CR). Two sun gears nsA, nsB of the planetarygear trains have a common rotational axle nss while a planet gearcarrier and a ring gear nrB of the planetary gear trains have a commonrotational axle nrsB. The two common rotational axles nss, nrsB performas the second rotational axle AD of the first planetary gear train 1(free transmission end in FIG. 2A or first power input end in FIG. 2B)and the second rotational axle BD of the second planetary gear train 2(first power input end in FIG. 2A or free transmission end in FIG. 2B).

Although the invention has been described in detail with reference toits presently preferred embodiment, it will be understood by one ofordinary skill in the art that various modifications can be made withoutdeparting from the spirit and the scope of the invention, as set forthin the appended claims.

What is claimed is:
 1. An independently controllable transmissionmechanism comprising: a first planetary gear train including a firstpower output end; a second planetary gear train connected with the firstplanetary gear train, the second planetary gear train including atransmission control end; a first power input end provided on the secondplanetary gear train; and a free transmission end provided on the firstplanetary gear train; wherein the transmission control end is used tocontrol the free transmission end to be functioned as a second powerinput end or a second power output end.
 2. The independentlycontrollable transmission mechanism as defined in claim 1, wherein eachof the first planetary gear train and the second planetary gear trainhas a positive speed ratio.
 3. The independently controllabletransmission mechanism as defined in claim 1, wherein each of the firstplanetary gear train and the second planetary gear train has a negativespeed ratio.
 4. The independently controllable transmission mechanism asdefined in claim 1, wherein the first planetary gear train has apositive speed ratio while the second planetary gear train has anegative speed ratio.
 5. The independently controllable transmissionmechanism as defined in claim 1, wherein the first planetary gear trainhas a negative speed ratio while the second planetary gear train has apositive speed ratio.
 6. The independently controllable transmissionmechanism as defined in claim 1, wherein the first planetary gear trainincludes a first rotational axle, a second rotational axle and a thirdrotational axle; the first rotational axle of the first planetary geartrain performed as the first power output end, the second rotationalaxle of the first planetary gear train performed as the freetransmission end, and the third rotational axle of the first planetarygear train connected with the second planetary gear train; and whereinthe second planetary gear train includes a first rotational axle, asecond rotational axle and a third rotational axle; the first rotationalaxle of the second planetary gear train performed as the transmissioncontrol end, the second rotational axle of the second planetary geartrain performed as the first power input end, and the third rotationalaxle of the second planetary gear train connected with the firstplanetary gear train.
 7. An independently controllable transmissionmechanism comprising: a first planetary gear train including a firstpower output end; a second planetary gear train connected with the firstplanetary gear train, the second planetary gear train including atransmission control end; a first power input end provided on the firstplanetary gear train; and a free transmission end provided on the secondplanetary gear train; wherein the transmission control end is used tocontrol the free transmission end to be functioned as a second powerinput end or a second power output end.
 8. The independentlycontrollable transmission mechanism as defined in claim 7, wherein eachof the first planetary gear train and the second planetary gear trainhas a positive speed ratio.
 9. The independently controllabletransmission mechanism as defined in claim 7, wherein each of the firstplanetary gear train and the second planetary gear train has a negativespeed ratio.
 10. The independently controllable transmission mechanismas defined in claim 7, wherein the first planetary gear train has apositive speed ratio while the second planetary gear train has anegative speed ratio.
 11. The independently controllable transmissionmechanism as defined in claim 7, wherein the first planetary gear trainhas a negative speed ratio while the second planetary gear train has apositive speed ratio.
 12. The independently controllable transmissionmechanism as defined in claim 7, wherein the first planetary gear trainincludes a first rotational axle, a second rotational axle and a thirdrotational axle; the first rotational axle of the first planetary geartrain performed as the first power output end, the second rotationalaxle of the first planetary gear train performed as the first powerinput end, and the third rotational axle of the first planetary geartrain connected with the second planetary gear train; and wherein thesecond planetary gear train includes a first rotational axle, a secondrotational axle and a third rotational axle; the first rotational axleof the second planetary gear train performed as the transmission controlend, the second rotational axle of the second planetary gear trainperformed as the free transmission end, and the third rotational axle ofthe second planetary gear train connected with the first planetary geartrain.
 13. An independently controllable transmission mechanismcomprising: two planetary gear trains connected each other; a firstpower output end provided on the combination of the two planetary geartrains; a transmission control end provided on the combination of thetwo planetary gear trains; a first power input end provided on thecombination of the two planetary gear trains; and a free transmissionend provided on the combination of the two planetary gear trains;wherein the transmission control end is used to control the freetransmission end to be functioned as a second power input end or asecond power output end.
 14. The independently controllable transmissionmechanism as defined in claim 13, wherein each of the two planetary geartrains has a positive speed ratio.
 15. The independently controllabletransmission mechanism as defined in claim 13, wherein each of the twoplanetary gear trains has a negative speed ratio.
 16. The independentlycontrollable transmission mechanism as defined in claim 13, wherein oneof the two planetary gear trains has a positive speed ratio while theother has a negative speed ratio.
 17. The independently controllabletransmission mechanism as defined in claim 13, wherein the combinationof the two planetary gear trains includes a first rotational axle, asecond rotational axle, a third rotational axle, a fourth rotationalaxle, a fifth rotational axle and a sixth rotational axle; and whereinthe first rotational axle performed as the first power output end, thesecond rotational axle performed as the free transmission end, the thirdrotational axle connected between the two planetary gear trains, thefourth rotational axle performed as the transmission control end, thefifth rotational axle performed as the first power input end, and thesixth rotational axle connected between the two planetary gear trains.18. The independently controllable transmission mechanism as defined inclaim 13, wherein the combination of the two planetary gear trainsincludes a first rotational axle, a second rotational axle, a thirdrotational axle, a fourth rotational axle, a fifth rotational axle and asixth rotational axle; and wherein the first rotational axle performedas the first power output end, the second rotational axle performed asthe first power input end, the third rotational axle connected betweenthe two planetary gear trains, the fourth rotational axle performed asthe transmission control end, the fifth rotational axle performed as thefree transmission end, and the sixth rotational axle connected betweenthe two planetary gear trains.